JPH0138955B2 - - Google Patents
Info
- Publication number
- JPH0138955B2 JPH0138955B2 JP17490980A JP17490980A JPH0138955B2 JP H0138955 B2 JPH0138955 B2 JP H0138955B2 JP 17490980 A JP17490980 A JP 17490980A JP 17490980 A JP17490980 A JP 17490980A JP H0138955 B2 JPH0138955 B2 JP H0138955B2
- Authority
- JP
- Japan
- Prior art keywords
- flow rate
- hydraulic pump
- feed
- rotary
- signal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000005553 drilling Methods 0.000 claims description 30
- 230000007246 mechanism Effects 0.000 claims description 13
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 235000019738 Limestone Nutrition 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000006028 limestone Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005065 mining Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
Landscapes
- Drilling And Exploitation, And Mining Machines And Methods (AREA)
- Earth Drilling (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、回転式穿孔機の制御装置に関し、
特に、ドリル回転用油圧ポンプの吐出圧と流量と
を検知して、その吐出流量を制御し、また、送り
用油圧ポンプの流量を検知してこれを定常値を比
較演算することにより、その吐出流量を制御し、
原動機の停止をなくし、且つ原動機出力を有効に
利用できるようにする。[Detailed Description of the Invention] [Industrial Application Field] This invention relates to a control device for a rotary drilling machine,
In particular, by detecting the discharge pressure and flow rate of the hydraulic pump for rotating the drill and controlling the discharge flow rate, and by detecting the flow rate of the feed hydraulic pump and calculating it by comparing it with a steady value, the discharge pressure and flow rate can be controlled. control the flow rate,
To eliminate the stoppage of a prime mover and to effectively utilize the output of the prime mover.
一般に、回転式穿孔機は、露天堀における石灰
石、石炭、鉱石等の採堀、又は軟弱地盤の改良工
法等の穿孔作業に広く使用されている。
In general, rotary drilling machines are widely used for drilling operations such as mining of limestone, coal, ore, etc. in open pits, or methods for improving soft ground.
また回転式穿孔器の油圧駆動装置は、各油圧ア
クチユエータ用の油圧ポンプを、夫々可変容量形
油圧ポンプとし、各油圧ポンプの最大出力を夫々
一定とする油圧制御方式等が採用されている。 Further, the hydraulic drive device for the rotary perforator employs a hydraulic control system in which the hydraulic pumps for each hydraulic actuator are variable displacement hydraulic pumps, and the maximum output of each hydraulic pump is kept constant.
この場合、各種のアクチユエータ用油圧ポンプ
は、各々分割したその出力の範囲で穿孔作業が可
能であり、夫々の負荷の変動に対して敏感に作動
するが、各ポンプが独立して制御されているた
め、最大の穿孔トルクによる穿孔時には、出力合
計が原動機の定格出力を超えるおそれがある。そ
こで、従来の油圧駆動装置は、最大の穿孔トルク
による穿孔時のエンジンストツプを防止するため
に、自動的に、又は勘による人力操作で急激に低
回転となるように構成されている。したがつて、
穿孔能率が低下するという問題点があつた。
In this case, the various actuator hydraulic pumps can perform drilling work within their divided output ranges, and operate sensitively to changes in their respective loads, but each pump is independently controlled. Therefore, when drilling with the maximum drilling torque, the total output may exceed the rated output of the prime mover. Therefore, in order to prevent the engine from stopping during drilling due to the maximum drilling torque, conventional hydraulic drive devices are configured to suddenly reduce the rotation speed automatically or by manual operation based on intuition. Therefore,
There was a problem that drilling efficiency decreased.
而して、これらの回転式穿孔機は、不特定な作
業条件のもとで穿孔作業をするので、作業者は計
器盤と穿孔状況とを監視しながら勘に頼る手動操
作を行わなければならず、しかも経験ある運転者
を必要とし、またその運転者の疲労も大きいとい
う問題点もあつた。 Since these rotary drilling machines perform drilling work under unspecified working conditions, the operator must perform manual operations relying on intuition while monitoring the instrument panel and drilling status. Furthermore, there was a problem in that it required an experienced driver, and the driver was highly fatigued.
この発明は、回転式穿孔機のかかる問題点を解
決するものであり、その目的は、穿孔機の油圧駆
動が原動機の定格出力を超える場合には自動的に
過負荷を防止するにあり、またその目的は、穿孔
トルクを略一定にして穿孔能率の向上を図るにあ
り、更にその目的は、原動機の出力を最大限に有
効利用することにある。 This invention solves this problem with rotary drilling machines, and its purpose is to automatically prevent overload when the hydraulic drive of the drilling machine exceeds the rated output of the prime mover, and The purpose of this is to improve the drilling efficiency by keeping the drilling torque substantially constant, and the purpose is to make maximum effective use of the output of the prime mover.
この発明は、かかる問題を解決するために、例
えば図示する実施例のように、回転用油圧ポンプ
と送り用油圧ポンプとを、夫々サーボ機構１７，
２０付きの可変容量ポンプとした回転式穿孔機の
制御装置において、
前記回転用油圧ポンプの吐出圧を検出する回転
圧力センサ１０と、前記回転用油圧ポンプの流量
を検出する回転流量センサ１１と、前記送り用油
圧ポンプの吐出圧を検出する圧力センサ１２と、
前記送り用油圧ポンプの流量を検出する送り流量
センサ１３と、前記回転圧力センサ１０で検出さ
れた前記回転用油圧ポンプの圧力信号及び回転流
量センサ１１で検出された前記回転用油圧ポンプ
の流量信号から前記回転用油圧ポンプの回転用所
要動力を演算するとともに、前記送り圧力センサ
１２で検出された前記送り用油圧ポンプの送り圧
力信号及び前記送り流量センサ１３で検出された
前記送り用油圧ポンプの流量信号から送り用所要
動力を計算し、更に前記回転用所要動力と送り用
所要動力とを積算して合計所要動力信号を送出す
る演算手段１４と、原動機の定格出力が設定され
この設定値信号を送出する定格出力設定手段１６
と、前記合計所要動力信号を定格出力の設定値信
号と比較して回転用油圧ポンプの流量を制御する
制御信号を回転用油圧ポンプのサーボ機構１７に
送出する第１の比較演算手段１５と、送り用油圧
アクチユエータの定常流量が設定されその設定信
号を送出する定常流量設定手段１８と、前記送り
流量センサ１３で検出された流量信号を前記定常
流量の設定値信号と比較して送り用油圧ポンプの
流量を制御する制御信号を送り用油圧ポンプのサ
ーボ機構２０に送出する第２の比較演算手段１９
と、
からなる回転式穿孔機の制御装置を提供する。
In order to solve this problem, the present invention, for example, as in the illustrated embodiment, connects a rotary hydraulic pump and a feeding hydraulic pump to a servo mechanism 17,
20, a control device for a rotary drilling machine as a variable displacement pump equipped with a rotary pressure sensor 10 for detecting the discharge pressure of the rotary hydraulic pump; a rotary flow rate sensor 11 for detecting the flow rate of the rotary hydraulic pump; a pressure sensor 12 that detects the discharge pressure of the feed hydraulic pump;
A feed flow rate sensor 13 that detects the flow rate of the feed hydraulic pump, a pressure signal of the rotary hydraulic pump detected by the rotary pressure sensor 10, and a flow rate signal of the rotary hydraulic pump detected by the rotary flow rate sensor 11. The required power for rotation of the rotary hydraulic pump is calculated from the above, and the feed pressure signal of the feed hydraulic pump detected by the feed pressure sensor 12 and the feed pressure signal of the feed hydraulic pump detected by the feed flow rate sensor 13 are calculated. Calculating means 14 calculates the required power for feeding from the flow rate signal, further integrates the required power for rotation and the required power for feeding, and sends out a total required power signal, and the rated output of the prime mover is set and the set value signal is calculated. Rated output setting means 16 for sending out
and a first comparison calculation means 15 that compares the total required power signal with a set value signal of the rated output and sends a control signal for controlling the flow rate of the rotary hydraulic pump to the servo mechanism 17 of the rotary hydraulic pump; a steady flow rate setting means 18 for setting the steady flow rate of the feed hydraulic actuator and sending out a setting signal; and a steady flow rate setting means 18 for setting the steady flow rate of the feed hydraulic actuator and sending out a setting signal thereof; A second comparison calculation means 19 sends a control signal for controlling the flow rate of the feed hydraulic pump to the servo mechanism 20 of the feed hydraulic pump.
A control device for a rotary drilling machine is provided.
演算手段１４によつて、回転圧力センサ１０か
らの回転用油圧ポンプの吐出圧力信号及び回転流
量センサ１１からの前記回転用油圧ポンプの流量
信号を受けて前記回転用油圧ポンプの回転用所要
動力を計算されるとともに、送り圧力センサ１２
からの前記送り用油圧ポンプの吐出し圧力信号及
び前記送り流量センサ１３からの前記送り用油圧
ポンプの流量信号を受けて送り用所要動力が計算
され、而して更に、前記回転用所要動力と送り用
所要動力とが積算されて合計所要動力値信号や送
出される。
The calculation means 14 receives the discharge pressure signal of the rotary hydraulic pump from the rotary pressure sensor 10 and the flow rate signal of the rotary hydraulic pump from the rotary flow rate sensor 11, and calculates the required power for rotation of the rotary hydraulic pump. is calculated and the feed pressure sensor 12
The required power for feeding is calculated in response to the discharge pressure signal of the hydraulic pump for feeding and the flow rate signal of the hydraulic pump for feeding from the feed flow rate sensor 13, and further, the required power for rotation and the flow rate signal of the hydraulic pump for feeding are calculated. The required power for feeding is integrated and a total required power value signal is sent out.
この演算手段１４の合計所要動力値信号は、第
１の比較演算手段１５に送出される。この第１の
比較演算手段１５は、原動機の定格設定値信号を
送出する定格設定設定手段１６に接続されている
ので、そこで、その定格信号設定手段１６が送出
する定格設定値信号と前記合計所要動力値信号と
が比較演算される。この比較演算値が、前記回転
用油圧ポンプの流量の増減の制御信号として、前
記回転用油圧ポンプのサーボ機構１７に送出さ
れ、回転用油圧ポンプが制御される。 The total required power value signal of the calculation means 14 is sent to the first comparison calculation means 15. Since this first comparison calculation means 15 is connected to a rating setting setting means 16 that sends out a rated setting value signal of the prime mover, it compares the rated setting value signal sent out by the rating signal setting means 16 with the total required value. A comparison operation is performed with the power value signal. This comparison calculation value is sent to the servo mechanism 17 of the rotary hydraulic pump as a control signal for increasing or decreasing the flow rate of the rotary hydraulic pump, and the rotary hydraulic pump is controlled.
また、前記送り流量センサ１３は、更に、第２
の比較演算手段１９に接続しており、この第２の
比較演算手段１９は、送り用油圧アリチユエータ
を作動するために必要な定常流量を設定してその
定常流量信号として送出する定常流量設定手段１
８が接続されていて、この定常流量設定手段１８
からの定常流量信号と前記送り流量センサ１３か
らの流量信号とを比較演算して、送り用油圧ポン
プの流量の制御信号とする。この制御信号が送り
用油圧ポンプのサーボ機構２０に送出されて、送
り用油圧ポンプが制御される。 Further, the feed flow rate sensor 13 further includes a second
The second comparison calculation means 19 is connected to the steady flow rate setting means 1 which sets the steady flow rate necessary for operating the feed hydraulic pressure unit and sends it out as a steady flow rate signal.
8 is connected, and this steady flow rate setting means 18
The steady flow rate signal from the feed flow rate sensor 13 is compared with the flow rate signal from the feed flow rate sensor 13, and the result is used as a control signal for the flow rate of the feed hydraulic pump. This control signal is sent to the servo mechanism 20 of the feed hydraulic pump to control the feed hydraulic pump.
この発明の実施例を図面にしたがつて説明す
る。
Embodiments of the invention will be described with reference to the drawings.
第１図は回転式穿孔器の全体立面を示してお
り、走行可能な機体１上にマスト２が装架されて
おり、穿孔機本体３はビツト４付きのロツド５を
担持してマスト２上に乗駕し、このマスト２に沿
つて滑動できるようになつている。穿孔機本体３
には、回転用油圧油圧モータ６を備えており、回
転用油圧モータ６の回転によつて減速歯車を介し
てロツド５に回転を与える。 Figure 1 shows the overall elevation of a rotary perforator, in which a mast 2 is mounted on a movable machine body 1, a perforator main body 3 carries a rod 5 with a bit 4, and the mast 2 It is designed to be able to ride on top and slide along this mast 2. Drilling machine body 3
is equipped with a rotational hydraulic hydraulic motor 6, and the rotation of the rotational hydraulic motor 6 gives rotation to the rod 5 via a reduction gear.
また、マスト２に設けた送り用アクチユエータ
７の作動により、チエン８を介して穿孔機本体３
に推力を負荷して穿孔作業を行なう。 In addition, by the operation of the feed actuator 7 provided on the mast 2, the punching machine body 3 is moved through the chain 8.
Drilling work is performed by applying thrust to the
第２図には、この発明になる制御装置のブロツ
ク回路を示してある。 FIG. 2 shows a block circuit of the control device according to the invention.
これによれば、回転用油圧ポンプの吐出圧を検
出してこれを回転圧力信号P1として送出する回
転圧力センサ１０と、同回転用油圧ポンプにおけ
る流量を検出してこれを回転流量信号Q1として
送出する回転流量センサ１１と、送り用油圧ポン
プの吐出圧を検出してこれを送り圧力信号P2と
して送出する送り圧力センサ１２と、同送り用油
圧ポンプにおける流量を検出してこれを送り流量
信号Q2として送出する送り流量センサ１３とを、
演算手段１４に接続してある。この演算手段１４
では、回転圧力信号P1と、回転流量信号Q1とに
より、回転用油圧ポンプの回転用所要動力や計算
され、また、送り圧力信号P2と、送り流量信号
Q2とで、送り用所要動力が計算され、更に回転
用所要動力と送り用所要動力とで、合計所要動力
が積算され、その値が、回転用油圧ポンプと送り
用油圧ポンプとの各所要動力の合計所要動力信号
として送出される。この演算手段１４を、原動機
の定格出力が設定されこの設定値信号を送出する
定格出力設定手段１６に接続した第１の比較演算
手段１５に接続する。而して、この第１の比較演
算手段１５では、前記演手段１４から送出した合
計所要動力信号と定格出力の設定値信号と比較演
算され、回転用油圧ポンプの制御信号として送出
される。この第１の比較演算手段１５は、更に回
転用油圧ポンプのサーボ機構１７に接続してい
る。而して、第１の比較演算手段１５が送出する
制御信号によりサーボ機構１７が制御され、回転
用油圧ポンプの回転が制御される。 According to this, a rotary pressure sensor 10 detects the discharge pressure of a rotary hydraulic pump and sends it out as a rotary pressure signal P1 , and a rotary pressure sensor 10 detects the flow rate in the rotary hydraulic pump and sends it as a rotary flow rate signal Q1. A rotary flow rate sensor 11 that detects the discharge pressure of the feed hydraulic pump and sends it out as a feed pressure signal P2 , and a feed pressure sensor 12 that detects the flow rate of the feed hydraulic pump and sends it as a feed pressure signal P2. A feed flow rate sensor 13 that sends out a flow rate signal Q2 ,
It is connected to the calculation means 14. This calculation means 14
Now, the required power for rotation of the rotary hydraulic pump is calculated from the rotation pressure signal P 1 and the rotation flow rate signal Q 1 , and the feed pressure signal P 2 and the feed flow rate signal
In Q 2 , the required power for feeding is calculated, and the total required power is integrated by the required power for rotation and the required power for feeding, and that value is calculated as the required power for each of the hydraulic pump for rotation and the hydraulic pump for feed. The total power required is sent out as a power signal. This calculation means 14 is connected to a first comparison calculation means 15 which is connected to a rated output setting means 16 which sets the rated output of the prime mover and sends out a set value signal. The first comparison calculation means 15 compares and calculates the total required power signal sent from the performance means 14 with the set value signal of the rated output, and sends it out as a control signal for the rotary hydraulic pump. This first comparison calculation means 15 is further connected to a servo mechanism 17 of a rotary hydraulic pump. The servo mechanism 17 is controlled by the control signal sent by the first comparison calculation means 15, and the rotation of the rotational hydraulic pump is controlled.
また、一方のドリルを所定の推力で前進させて
穿孔作業をする場合、送り用油圧アクチユエータ
７を作動させるために必要な定常流量Q2′を設定
して送出する定常流量設定手段１８からの定常流
量Q2′と、前記送り用油圧ポンプの送り流量セン
サ１３から送出される送り流量信号Q2とを、第
２の比較演算手段１９で比較演算比較演算する。 In addition, when performing drilling work by moving one drill forward with a predetermined thrust, a steady flow rate setting means 18 that sets and sends a steady flow rate Q 2 ' necessary to operate the feed hydraulic actuator 7 is used. The flow rate Q 2 ' and the feed flow rate signal Q 2 sent from the feed flow rate sensor 13 of the feed hydraulic pump are subjected to a comparison calculation by a second comparison calculation means 19.
この第２の比較演算手段１９で算出した演算値
を制御信号として送り用油圧ポンプのサーボ機構
２０を制御する。 The servo mechanism 20 of the feed hydraulic pump is controlled using the calculated value calculated by the second comparison calculation means 19 as a control signal.
かくして、過剰流量による動力増大を防止し、
適正の送りにて実際の穿孔に追従させるようにポ
ンプの流量制御が行われる。 In this way, power increase due to excessive flow rate is prevented,
The flow rate of the pump is controlled so as to follow the actual drilling with an appropriate feed.
この発明によれば、一定の推力で、穿孔時に岩
質等の作業条件の変化に対して回転数を制御しな
がら最大トルクにて穿孔することが可能であり、
従来のように、所定の穿孔動力以内における穿孔
作業で原動機の出力不足やエンジンストツプ等の
不具合を生じることなく、原動機の出力を最大限
に有効利用することができる。
According to this invention, it is possible to perform drilling with a constant thrust and maximum torque while controlling the rotation speed in response to changes in working conditions such as rock quality during drilling,
Unlike conventional drills, the output of the prime mover can be utilized effectively to the maximum extent without causing problems such as insufficient output of the prime mover or engine stop during drilling operations within a predetermined drilling power.
また、運転者は、勘に頼る計器操作の疲労から
開放され、動力の有効利用により穿孔能率を向上
することができる。 In addition, the driver is freed from the fatigue of operating instruments that rely on intuition, and drilling efficiency can be improved by effectively utilizing power.
第１図は、回転式穿孔機の全体立面図、第２図
は、制御装置のブロツク回路図である。
図中、７は送り用油圧アクチユエータ、１０，
１２は、夫々回転圧力センサと回転流量センサ、
１１，１３は、夫々送り圧力センサと送り流量セ
ンサ、１４は演算手段、１５は第１の比較演算手
段、１６は定格出力の設定手段、１７は回転用油
圧ポンプのサーボ機構、１８は定常流量の設定手
段、１９は第２の比較演算手段、２０は送り用油
圧ポンプのサーボ機構である。
FIG. 1 is an overall elevational view of the rotary drilling machine, and FIG. 2 is a block circuit diagram of the control device. In the figure, 7 is a feed hydraulic actuator, 10,
12 are a rotational pressure sensor and a rotational flow rate sensor, respectively;
11 and 13 are a feed pressure sensor and a feed flow rate sensor, respectively, 14 is a calculation means, 15 is a first comparison calculation means, 16 is a rated output setting means, 17 is a servo mechanism of a rotating hydraulic pump, and 18 is a steady flow rate. 19 is a second comparison calculation means, and 20 is a servo mechanism of a hydraulic pump for feeding.
Claims (1)
夫々サーボ機構１７，２０付きの可変容量ポンプ
とした回転式穿孔機の制御装置において、 前記回転用油圧ポンプの吐出圧を検出する回転
圧力センサ１０と、前記回転用油圧ポンプの流量
を検出する回転流量センサ１１と、前記送り用油
圧ポンプの吐出圧を検出する送り圧力センサ１２
と、前記送り用油圧ポンプの流量を検出する送り
流量センサ１３と、前記回転圧力センサ１０で検
出された前記回転用油圧ポンプの圧力信号及び回
転流量センサ１１で検出された前記回転用油圧ポ
ンプの流量信号から前記回転用油圧ポンプの回転
用所要動力を演算するとともに、前記送り圧力セ
ンサ１２で検出された前記送り用油圧ポンプの送
り圧力信号及び前記送り流量センサ１３で検出さ
れた前記送り用油圧ポンプの流量信号から送り用
所要動力を計算し、更に前記回転用所要動力と送
り用所要動力とを積算して合計所要動力信号を送
出する演算手段１４と、原動機の定格出力が設定
されこの設定値信号を送出する定格出力設定手段
１６と、前記合計所要動力信号を定格出力の設定
値信号と比較して回転用油圧ポンプの流量を制御
する制御信号を回転用油圧ポンプのサーボ機構１
７に送出する第１の比較演算手段１５と、送り用
油圧アクチユエータの定常流量が設定されその設
定信号を送出する定常流量設定手段１８と、前記
送り流量センサ１３で検出された流量信号を前記
定常流量の設定値信号と比較して送り用油圧ポン
プの流量を制御する制御信号を送り用油圧ポンプ
のサーボ機構２０に送出する第２の比較演算手段
１９と、 からなる回転式穿孔機の制御装置。[Scope of Claims] 1. In a control device for a rotary drilling machine in which a rotary hydraulic pump and a feeding hydraulic pump are variable displacement pumps with servo mechanisms 17 and 20, respectively, the discharge pressure of the rotary hydraulic pump is detected. a rotary pressure sensor 10 that detects the flow rate of the rotary hydraulic pump, a rotary flow rate sensor 11 that detects the flow rate of the rotary hydraulic pump, and a feed pressure sensor 12 that detects the discharge pressure of the feed hydraulic pump.
, a feed flow rate sensor 13 that detects the flow rate of the feed hydraulic pump, a pressure signal of the rotary hydraulic pump detected by the rotary pressure sensor 10, and a pressure signal of the rotary hydraulic pump detected by the rotary flow rate sensor 11. The required power for rotation of the rotary hydraulic pump is calculated from the flow rate signal, and the feed pressure signal of the feed hydraulic pump detected by the feed pressure sensor 12 and the feed oil pressure detected by the feed flow rate sensor 13 are calculated. A calculation means 14 calculates the required power for feeding from the flow rate signal of the pump, and further integrates the required power for rotation and the required power for feeding to send out a total required power signal, and the rated output of the prime mover is set. a rated output setting means 16 that sends out a value signal, and a servo mechanism 1 of the rotary hydraulic pump that compares the total required power signal with a set value signal of the rated output and outputs a control signal that controls the flow rate of the rotary hydraulic pump.
7, a steady flow rate setting means 18 which sets the steady flow rate of the feed hydraulic actuator and sends out a setting signal thereof, and a flow rate signal detected by the feed flow rate sensor 13, A control device for a rotary drilling machine, comprising: a second comparison calculation means 19 for sending a control signal for controlling the flow rate of the feed hydraulic pump to the servo mechanism 20 of the feed hydraulic pump by comparing it with a flow rate set value signal; .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17490980A JPS57100292A (en) | 1980-12-11 | 1980-12-11 | Control apparatus of rotary drilling machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17490980A JPS57100292A (en) | 1980-12-11 | 1980-12-11 | Control apparatus of rotary drilling machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57100292A JPS57100292A (en) | 1982-06-22 |
| JPH0138955B2 true JPH0138955B2 (en) | 1989-08-17 |
Family
ID=15986809
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17490980A Granted JPS57100292A (en) | 1980-12-11 | 1980-12-11 | Control apparatus of rotary drilling machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57100292A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6154096U (en) * | 1984-09-11 | 1986-04-11 | ||
| JP2581739Y2 (en) * | 1990-12-29 | 1998-09-24 | 箱竹 株式会社 | Multipurpose rack |
-
1980
- 1980-12-11 JP JP17490980A patent/JPS57100292A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57100292A (en) | 1982-06-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CA1084900A (en) | Controls for hydraulic percussion drill | |
| US4006783A (en) | Hydraulic operated rock drilling apparatus | |
| US4793421A (en) | Programmed automatic drill control | |
| CN101755102B (en) | Constant-mode auto-drill with pressure derivative control | |
| US3823784A (en) | Method and apparatus for controlling hydraulic drifters | |
| US4355691A (en) | Hydraulic drilling apparatus | |
| CN106468137A (en) | A kind of control system improving rotary digging drill power head operating rate and method | |
| JPH0138955B2 (en) | ||
| US6293359B1 (en) | Pressure control of a drilling apparatus | |
| US20180298753A1 (en) | Control system and method for controlling operation of an underground mining machine | |
| EP1499818B1 (en) | Arrangement for driving a compressor | |
| US12000281B2 (en) | Horizontal directional drilling system with improved system for limiting torque | |
| CN107795278B (en) | Speed limiting method for working device of pile driver and hydraulic speed limiting system | |
| JPS62156494A (en) | Controller of rock driller | |
| AU2019464016B2 (en) | Hydraulic system, mining machine and method of controlling hydraulic actuator | |
| US2259694A (en) | Diamond drill feed control | |
| CN105422094A (en) | Direct-drive hydraulic transmission coal mining machine cutting rotary drum height regulating system and method | |
| JPH0221603Y2 (en) | ||
| CA1090230A (en) | Controls for hydraulic percussion drill | |
| CN111894489A (en) | Drill rod control method and system and drilling machine | |
| JP3447108B2 (en) | Drilling machine rotation control device | |
| JPH04203506A (en) | Controller for hydraulic motor | |
| SU901499A2 (en) | Device for feed and rotation of boring tool | |
| CA2310893C (en) | Pressure control of a drilling apparatus | |
| JP2994076B2 (en) | Control device for hydraulic motor |